Shearing apparatus

ABSTRACT

A shearing apparatus for automatically shearing natural and/or synthetic fibrous material comprises a rotating blade and a fixed blade positioned in a cutting relationship with a minimal clearance space therebetween. Means are provided to accurately measure that clearance space while the apparatus is in operation. Means are also provided to accurately adjust the relative position of the cutting blades during the operation of the apparatus thereby to reduce the clearance space to a desired amount. A guide means which includes adjustment mechanisms for accurately positioning a guide table in two planes relative to the cutting blades is positioned adjacent the cutting blades and is effective to direct the material fibers at a suitable angle into the shearing zone between cutting blades. An exhaust system is positioned adjacent the rotating blade and efficiently removes the sheared segment of the fibers from the shearing zone.

[451 Aug. 15, 1972 1,649,172 ll/l927 Mason R FOREIGN PATENTS ORAPPLICATIONS 816,050 7/1959 Great Britain.....,.......308/3 A PrimaryExaminer-Robert R. Mackey Attorney-James & Franklin [57] v ABSTRACT Ashearing apparatus for automatically shearing natural and/or syntheticfibrous material comprises a rotating blade and a fixed blade positionedin a cutting relationship with a minimal clearance space therebetween.Means are provided to accurately measure that clearance space while theapparatus is in operation. Means are also provided to accurately adjustthe relative position of the cutting blades during the operation of theapparatus thereby to reduce the SHEARWG APPARATUS Aaron M. Kaufman,Rosedale, N.Y.

Machine Works, Inc., Brooklyn, NY.

May 26, 1970 .26/15 R, 308/3 A .D06c 13/00 .26/15 R, 15 L, 15 EB, 68;308/3 A; 74/509 References Cited UNITED STATES PATENTS llnited StatesPatent Kaufman [72] Inventor:

[73] Assignee: Reliable [22] Filed:

21 Appl.No.: 40,609

[58] FieldofSearch..........

clearance space to a desired amount. A guide means which includesadjustment mechanisms for accurately positioning a guide table in twoplanes relative to the cutting blades is positioned adjacent the cuttingblades and is effective to direct the material fibers at a suitableangle into the shearing zone between cutting blades. An exhaust systemis positioned adjacent the rotating blade and efiiciently removes thesheared segment of the fibers from the shearing zone.

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sum 8 BF 8 i u R /58 INVENTOR AARON M. KAUFMAN ATTORNEY SHEARINGAPPARATUS This invention relates to shearing devices, and morespecifically to an apparatus which is adapted to shear natural and/orsynthetic fibers continuously or intermittently by the rotary motion ofa shearing blade.

Generally, a shearing action is accomplished by placing the object to besheared between two blades so that a single point of contact issimultaneously made between each blade and the object when the object isbrought toward the blades. When further pressure is exerted on theobject by the blades after contact is made, the surfaces of the objectin contact with the blades are compressed until the maximum point ofelasticity is reached. Beyond this point, the blades penetrate thesurfaces of the object. Continued movement of the blades toward eachother develops a force of an intensity sufficient to overcome molecularorder within the structure of the object. At that point the part of thethickness of the object which is not yet penetrated by the blades breaksaway and the object is said to have been sheared. Normally, thepercentage of the object that is broken away in this manner approximates30 percent of the total material thickness. This percentageapproximation generally applies for all types of material or fibersbeing sheared.

While the above action of shearing has been described with reference totwo moving blades, present devices which are adapted to shear on a widescale production basis function in essentially the same waynotwithstanding a structure in which only one blade moves and the otherblade is fixed. A typical device of this type includes a rotatingcylinder, the periphery of which is equipped with a plurality of cuttingblades. The fixed blade is commonly referred to as a bedknife and ispositioned at a precise location relative to the rotating blades. A flatguide table or plate is positioned near the bedknife and is adapted tocarry the material to be sheared toward the bedknife. The end of thistable or plate is provided with an extended part over which the materialis passed during its movement. This extended part is positioned veryclose to the bedknife and is effective to spread the fabric so that thefibers to be sheared are projected into an overlapping engagement withthe stationary bedknife. The blades on the rotating cylinder then engagethese overlapping fibers at a surface thereof opposite to the surfacewhich engages the fixed blade, and shearing of the fibers occurs.Continuous shearing action is accomplished by moving the fibers throughthe shearing zone at a desired rate of speed while simultaneouslyrotating the cylinder at a suitable speed relative to the movement ofthe fabric.

In order to effect a proper shear of the fibers in accordance with theprinciples above discussed, precise positioning of the variouscomponents in the shearing apparatus is essential. Normally there shouldbe virtually no clearance at the shearing zone between the cuttingblades to uniformly cut the fibers and thereby establish a fine finishon the fabric. For example, the clearance between fixed and rotatingcutting blades in this area should be maintained at some value equal toor less than the molecular breakaway thickness of the material, that is30 percent or less of the thickness of the fiber for good shearingaction. Maintaining such a small clearance between cutting blades hasthus far been a major problem in shearing devices of this type.

The primary difficulty is that there are many apparatus structuralvariables which influence this particular clearance setting and must becontrolled. Moreover, the fiber thickness is rarely uniform from fabricto fabric or even in a single fabric which is to be sheared. Extra finefabrics include fibers having a thickness as small as 0.0001 inch. Thus,the clearance should be maintained at a level which essentially is forall practical measuring purposes no clearance at all, and yet there mustbe no frictional interference between the rotating blade and the fixedblade.

Attempts to overcome the difficulties of maintaining such a slightclearance between working blades have thus far not been satisfactory. Inaddition to the fiber thickness variation and structural problemsanother major difficulty has been the general inability to prevent theflyout action of the rotating blades on the cylinder. These bladesextend several thousandths of an inch outwardly during rotation due tothe centrifugal force acting upon them. This must be taken into accountwhen the initial setting of the blades is made. However, the initialsetting is made when the blades are at rest, and therefore is merely anestimated position. Adjustment of the cylinder blade while it isrotating is not good practice since damage of the cutting blades is verypossible. With many shearing devices such adjustment is not evenpossible because of the nature of the structure and even if it werepossible, there is no successful way to accurately determine whether asuitable adjustment has been made.

Other problems which have a strong influence upon the proper operationof the shearing apparatus have also thus far escaped solution. Amongsuch problems is the fact that the cylinder and its supporting structureis subject to vibrational forces because of the high speed at which thecylinder is rotated. Obviously such vibration is most undesirable andmay seriously adversely affect the quality of the finished product.Still another consideration is the specific position of the guide tablerelative to the cylinder blades. This position is important since it isdeterminative of the position of the fibers as they enter the shearingzone. Yet just as with the blade position, precise positioning of thiscomponent is also difficult to attain, in part because the movement ofany of the components is affected by the inherent inaccuracies of themechanism itself. For example, when the cylinder is moved mechanicallyto get its blades into a proper position, any calculated degree ofmovement must necessarily be affected by the backlash in the movingmechanism. HOwever, because of the size and inaccessibility of themovable components movement must be imparted by some driving means. As aresult lost motion is incurred and inaccuracies result. When clearancesin the order of a few thousandths of an inch and less are required, suchinaccuracies are significant in the system and must be avoided.

It is the primary object of this invention, therefore, to provide ashearing apparatus which overcomes all of the aforementioned problems,and which is capable of shearing fibrous materials of various types andsizes with a high degree of quality.

It is another object of this invention to provide a means for monitoringthe clearance space between shearing blades in a shearing apparatuswhile the apparatus is in motion.

It is a further object of this invention to provide a shearing apparatuswhich is structured so that the positions of the shearing blades may beadjusted relative to each other with a high degree of accuracy evenwhile the apparatus is in motion.

It is still another object of this invention to provide a shearingapparatus which is characterized by a unique construction which enablesit to resist vibration during its operation and thereby substantiallyeliminate the effects of vibrational forces on the shearing action.

It is yet another object of this invention to provide a shearingapparatus which is characterized by a guide table having adjustmentmeans adapted to vary the position of the table in several planes.

It is still a further object of this invention to provide a shearingapparatus having an exhaust system which is capable of removing flockfrom the shearing zone efficiently and quickly.

The shearing apparatus of the invention solves the aforementionedproblems and satisfies the above objects by a plurality of improvementsin a basic shearing apparatus comprising a rotating blade and a fixedblade. One such improvement permits the apparatus to be monitored forclearance space between the blades while the apparatus is in operationand enables an adjustment of the shearing components to be made basedupon the monitoring information received while the apparatus is inoperation. To this end means for measuring the distance between the edgeof the blade on the rotating cylinder and the edge of the fixed cuttingblade comprise an electrical power source, preferably a voltage sourceof a small nominal voltage, which is connected at one output terminal tothe bedknife and at the other output terminal to the bearings whichcarry the cylinder. The cylinder blades are electrically connected tothe bearings. An insulating material is used to electrically isolate thecylinder blades from the bedknife. An indicating means such as a light,a voltmeter or the like is connected in the circuit. When a voltage fromthe source is applied, the dielectric between bedknife and cylinderblade will be broken down provided that the clearance is small enoughfor such action to occur. When the breakdown of the dielectric doesoccur it is indicated at the light or meter in the form of a currentflow, the intensity of which is directly proportional to the degree ofbreakdown of the dielectric. Thus, if the blades are actually incontact, a high current reading will be registered. On the other hand,if the clearance between blades is too great, no current or a veryminimal current will be measured. By a proper correlation of the voltageand current, the measuring instrument may be calibrated to indicate theclearance in dimensions as little as a few ten thousandths of an inch.Such an indication is readily obtained when the cylinder blades arerotating, since connection of the power source need not be made directlyto the rotating blades to obtain the desired results. Therefore theclearance space between blades in the shearing zone may be continuouslyand accurately monitored during the operation of the apparatus.

One section of the shearing apparatus of the invention is constructed asa unit to resist vibrational forces during the rotation of the cylinderand to facilitate the manufacture, assembly and transportation of thesystem. That section comprises the rotatable cylinder and bladesthereon, a pair of bearings, one at each end of the cylinder shaft,bearing support blocks on which the bearings are mounted, and speciallyconfigured supporting members on which the bearing blocks arepositioned. The supporting members are in turn affixed to the supportingplate which extends across the shearing apparatus for the full length ofthe cylinder. A bedknife holder is permanently and rigidly affixed tothat plate. The bedknife is adjustably secured to the bedknife holder ata predetermined angle relative to the cylinder. Yet another supportingplate is rigidly affixed to the first plate, and extends upwardly at anangle thereto to connect with the bedknife holder at the rear portionthereof. The resulting structure of bedknife and support platesresembles a triangle in cross section and it is this structure whichimparts an exceptional degree of rigidity to the overall assembly.

The specially configured supporting members which are positioned beneaththe bearing blocks are in the form of a block H. The upper parts of eachH block engages the lower projecting part of the bearing blocks. Thisengagement is effective to prevent lateral movement of the cylinder.However, forward and rearward movement of the cylinder toward and awayfrom the bedknife blade is accomplished by the linear movement of thebearing support blocks on the H blocks. This movement may be provided bya manual or automatic rotation of a driving shaft which is operativelyconnected to the cylinder bearings. A special locking mechanism isconnected between the H support blocks and the bearing support blocksand is effective to drive these blocks together and hold them in tightengagement after the desired movement of the cylinder is carried out.

A special feature of the shearing apparatus is the connecting mechanismbetween the driving shaft and the cylinder bearings which enables thecylinder to be moved an accurate amount in response to the motion ofthat shaft without lost motion of any kind. This mechanism comprises aspecially configured member operatively threadably engaging andsubstantially enclosing the shaft. This member is partially split,preferably at its central portion, and is provided with adjusting meanssuch as screws which pass through one split section. Tightening orloosening these screws adjusts the degree of engagement pressure betweenthe member and the threaded shaft, that pressure being capable ofadjustment to the extent necessary to eliminate backlash between theshaft and the threaded member. The member is rigidly affixed to thecylinder bearings which in turn engage the cylinder shaft. Upon themovement of the threaded shaft, the member is moved linearly along theshaft and that linear motion is transmitted directly to the bearings andthus the cylinder. The degree of cylinder movement may be accuratelycalculated in terms of shaft revolutions since lost motion iseliminated.

Additional parts of the shearing apparatus of the invention includeimprovements which are also designed to provide a control of thosevariable factors which influence the shearing operation. One componentwhich plays an important role in the operation of the apparatus is theguide plate or table which is used to guide into the shearing zone thematerial to be cut, and more specifically to spread that material sothat the fibers approach this shearing zone in an uncluttered condition.

It is imperative that this table, which is commonly referred to as anose box or nose piece, be positioned so that the desired length offiber is cut at an angle which is suitable to obtain a good shearingaction. In the present invention several improvements have beenincorporated in the nose piece structure to enable it to be positionedin several planes relative to the plane of the shearing zone. Means areprovided to move the nose piece toward or away from the cutting zone anexact amount. In addition other means are provided to move the nosepiece upwardly or downwardly relative to the cutting zone an amountwhich also may be accurately determined. In the preferred embodiment,the forward moving means comprises first and second tracks attached tothe frame of the apparatus on either side of the nose piece. Front andrear rollers are fixed to the nose piece and are adapted to roll in thetracks on the frame. The rollers are driven by a threaded shaft and geararrangement through an antibacklash member similar to that abovedescribed with reference to cylinder movement. The motion may occur bythe manual or automatic manipulation of the shaft.

In the preferred embodiment, the nose piece is constructed with an upperand a lower section. These sections are hinged at the rear part of thenose piece. An eccentric cam is positioned between upper and lowersections and engages the underside of the upper section. The cam iseffective when driven in a rotary direction to separate the sectionsabout the hinged con nection at the rear portion. The driving force tothe cam is also provided by a combination of a threaded shaft and a gearconnected to that shaft and working the cam. Since it has beendetermined that optimum shearing action occurs when the nose piececenter line is approximately one-eighth inch above the center line ofthe rotating cylinder, that exact position is readily obtained by thevertical movement of the upper section of the nose piece by the cammechanism. For this purpose a fixed scale may be provided on the frameof the apparatus itself in a position to accurately indicate when thenose piece has arrived at its proper operating level.

Another improvement in the shearing apparatus of the invention whichenables the apparatus to function more efficiently is the incorporationof a novel flock exhaust system. The system is constructed so as tocreate a negative pressure zone as close to the shearing zone aspossible. In addition, a high velocity exhaust zone which connects withthe lower portion of the rotating cylinder is also provided by a specialarrangement of exhaust manifolds. This high velocity zone enables bettercontrol and exhaust of the flock which results from fiber shearing.Heretofore, the flock became caught in the turbulence generated by therotating cylinder, and clogged the cutting blades to the extent thatthey were often rendered unusable. In the present apparatus, the exhaustsystem is effective to eliminate substantially all flock from theapparatus quickly and efficiently. In addition, the fibers of the fabricto be sheared are passed into the shearing zone at a controlled angle bythe suction force of the negative pressure zone. This helps to rigidifythe fibers so that they may more easily be sheared.

To the accomplishment of the above, and to such other objects as mayhereinafter appear, the present invention relates to a shearingapparatus as defined in the appended claims, and as described in theaccompanying drawings in which:

FIG. I is a perspective view of a shearing apparatus typical of theinvention;

FIG. 2 is a cross-sectional view of the shearing apparatus taken on theline 2-2 of FIG. 1;

FIG. 3 is a top plan view of the nose piece illustrated in FIG. 2, takenon the line 33 of FIG. 2;

FIG. 4 is a cross-sectional view of the nose piece illustrated in FIG.3, taken on the line 4-4 of FIG. 3;

FIG; 5 is an enlarged side elevational view of the nose pieceillustrated in FIGS. 3 and 4, taken on line 5--5 of FIG. 4;

FIG. 6 is a fragmentary view to a reduced scale of the nose pieceillustrated in FIGS. 3-5 in a fall away position on the frame of theapparatus of FIG. 1;

FIG. 7 is a fragmentary perspective view of a unitized structure whichforms a part of the shearing apparatus of FIG. 1; together with aschematic representation of a sensing means effective to measure theclearance distance between cutting blades in the apparatus;

FIG. 8 is a schematic illustration of the shearing operation of theapparatus of FIG. 1, the sensing means also being schematically shownthere;

FIG. 9 is a side elevational view, in some respects modified from theother views, of the driving systems employed in the operation of theshearing apparatus as viewed from the right side of FIG. 1;

FIG. 10 is a side elevational view of the driving means for fabric feed,of the embodiment of FIG. 9 as viewed from the left side of FIG. 1;

FIG. 11 is a front elevational view of the rotatable cutting blades on acylinder together with a support structure therefor which is adapted topermit linear movement of the cylinder;

FIG. 12 is a cross-sectional view of the support structure at the rightside of FIG. 11 as taken on the line 12-12 of FIG. 11; and

FIG. 13 is a fragmentary cross-sectional view of the same supportstructure of FIG. 12 taken on line 13-13 of FIG. 11.

Referring to FIG. 1, a shearing apparatus typical of the invention isgenerally designated by the numeral 10. The apparatus 10 comprises asupporting means generally designated 12 which in cross-sectioncomprises an A frame construction 13 as shown in FIG. 2. Support means12 includes the right-side support frame 14 and the left side supportframe 16. These support frame 14 and 16 are in the form of modularcabinets which house the driving mechanisms employed for the operationof the moving parts of the apparatus. These driving mechanisms are bestshown in FIG. 9 within frame 14 and in FIG. 10 within frame 116, accessthereto being obtained through doors l5 and 17, respectively.

A platform 18 which is equipped with a plurality of legs 20 positionedto support the platform on the floor is hingedly connected to thesupport means 12, and is capable of movement upwardly and inwardly inthe direction of the arrow 22 of FIG. 1 toward the side frames 14 and16. The platform may therefore be swung out of the way of the floor areawhen the apparatus is not in use and may be used to support an operatorwhen the apparatus is in use. A hood 24 positioned above the apparatus10 opposite the platform 18 is also capable of movement toward and awayfrom the body of the apparatus. This hood is shown in the open positionbut would be closed during the operation of the apparatus for the safetyof the operator as shown in FIG. 2. During that operation an oil mistgenerating unit 21 comprising a threaded shaft 23, a spray head 25movable along shaft 23 and effective to spray oil onto cutting blades 32of revolving cylinder 34, and a motor 27 (FIG. 10) effective to rotateshaft 23 also is in operation.

A plurality of rollers generally designated by the numeral 26 in FIG. 1are mounted by brackets 28 on the side frames 14 and 16, and extendsubstantially the entire distance between these frames. These rollers 26are employed to guide and drive the fabric to be cut towards a shearingzone or cutting area, generally designated 30 and to carry the fabricout of the apparatus after shearing. That shearing zone 30 isestablished at the location where the cutting blades 32 on a revolvingcylinder 34 come closest to a fixed cutting blade 36 which is mounted ona blade holder 38, as best shown in FIG. 8. A sheet fabric 29 is guidedtoward the zone 30 by the guide means 40 herein referred to as a feedtable. The nose piece 200 of that feed table is effective to pass thepile fibers 42 on fabric 29 into the zone 30 and to spread those fibersso that they reach the zone in an uncluttered condition and at asuitable cutting angle. As shown schematically in FIG. 8, the fibers 42overlap the edge 43 of the fixed cutting blade 36, and are sheared bythe action of the revolving blades 32 working against the fixed blade36. The fabric 29 as it passes out of the shearing zone 30 is thencharacterized by a surface of pile fibers having a uniform length.

The path traversed by the fabric 29 during its travel into and out ofthe shearing apparatus 10 is best seen by referring to FIG. 2. As thereillustrated the fabric 29 enters the apparatus below platform 18 andpasses over roller 44. It then proceeds upwardly to roller 46 and fromthere substantially horizontally to the feed table 40. As explained withreference to FIG. 8, the fabric 29 passes over the nose piece 200 pastthe shearing zone 30 and then to roller 48. Fabric 29 then continuesunder roller 50 upwardly to roller 52, downwardly over roller 54 toroller 56 where it once again moves upwardly over the roller 58 andoutwardly over the roller 60. The fabric then passes out of the machineand is collected by a suitable mechanism not shown but conventional.

Each of the rollers 44-60 performs a specific function in moving thefabric 29. Roller 44, for example, is a free-turning idler roller havingindividual bearings at each end. This roller is used only as a guide toproperly direct the entering fabric within the apparatus. Roller 46 ispivotally connected at one end to frame 16 at point 47 in FIG. 1, and ismovably connected at its opposite end to the bracket 49 on the frame 14.A knob 51 is connected by means of a shaft 53 (FIG. 2) to this rollerand when rotated adjusts the horizontal position of that end of theroller carried in bracket 49. This roller 46, which is covered withrubber for increased traction, is not motivated by a driving mechanism.It

may rotate freely or be controlled by a braking means. It is used toprovide the proper tension on the fabric as it passes into the machineand it also controls fabric tracking.

Roller 48 is also a free-rolling roller used to guide the fabric towardthe roller 50. The latter roller is driven by variable speed motor means55 partially shown in FIG. 10. THe roller 50 is connected to the motor55 by a sprocket 57 and a chain 59 through a slip clutch. As shown inFIG. 10 a second sprocket 61 mounted on a slip clutch 63 is alsoconnected to the motor 55 through the sprocket chain 59, and is of alarger diameter than sprocket wheel 57. Sprocket 61 is connected toroller 58, and due to the different sizes of sprocket wheels 57 and 61,roller 58 moves at a slightly faster rate of speed than does roller 50,thereby drawing the fabric out of the apparatus The remaining rollers52, 54, 56 and 60 are guide rollers which are freely rotatable inbearings connected by bearing brackets 28 to the side frames 14 and 16,as illustrated in FIG. I.

The shearing apparatus and its operation as thus far described do notdiffer substantially from conventional systems. In all such systems theshearing zone 30, that is the clearance space between cutting blades 32and 36, should be maintained at a minimum clearance level, that is equalto or less than 30 percent of the thickness of the fibers to be cut. Inreferring to FIG. 8, it will be appreciated that the clearance space maybe varied by relative movement of the cylinder 34 on which the cuttingblades 32 are mounted relative to the cutting blade 36. The cuttingblade 36 may be elevated or lowered by releasing bolts and turning theadjusting screws 62, but it is preferred that this adjustment bereversed for wear compensation of a more or less gross nature. Theclearance adjustment is preferably accomplished by moving the cylinder34 back and forth in the direction of the arrow in FIG. 8, by meansdescribed below, this being much more feasible for in-operationadjustment. In either case, the present invention includes means foraccurately measuring the clearance dimension during such movement, evenwhen the apparatus is in operation, that is, when the cylinder 34 isrotating.

Such a measurement is very simply accomplished in the present inventionby providing an electrical potential across the fixed cutting blade 36and the movable cutting blades 32. FIGS. 7 and 8 schematicallyillustrate this arrangement. As there shown, a voltage source 64 whichmay produce a voltage of a small magnitude, for example on the order of6 volts, is connected by wire 66 to an electrically conductive bearingblock 68. The bearing block 68 contains a bearing for carrying thecylinder 34, and more specifically the cylinder shaft 70, and iselectrically connected to the cutting blade 32 through the shaft 70 andthe body of the cylinder 34. All of these members are composed of anelectrically conductive material such as a suitable metal. Therefore oneterminal of the voltage source 64 is electrically connected to theblades 32. The other terminal of the voltage source 64 is connected toan indicating means such as a light or meter 72. Electrical connectionis made from the light to the fixed cutting blade 36 by the wire 74. Inpractice, such a connection may be made to a supporting block 76 asshown in FIG. 7. This block 76 is electrically conductive and is mountedon an electrically conductive base 78 to which the bedknife holder 38and thus the bedknife 36 are also connected. Since these members are allelectrically conductive, the voltage source 64 is connected to the fixedcutting blade 36. Blades 32 are insulated from blade 36 by insulation 75which is positioned between bearing block 68 and support block 94. As aresult, when the source 64 is energized, its output voltage is placeddirectly across the cutting blades and the means 72 is effective toindicate the level of current conduction between these blades. Sinceconduction between blades is directly dependent upon the size of the gapbetween blades, or stated differently, the magnitude of the dielectricbetween the blades, a good indication of the clearance space may beobtained by noting the current level in the means 72. Obviously, if theclearance space between blades is of the order of magnitude desired, acurrent will pass between the blades and register on the means 72. If,however, the gap is too large the means 72 will indicate no current flowor a current insufficient for the purposes of the proper operation ofthe machine. The means 72 may be consu'tuted by an indicating instrumentpositioned on the front panel of frame 14 as shown in FIG. 1 for theconvenience of the operator. Thus by the simple means described anindication of the gap between blades may be obtained while the machineis in operation, and due to improvement hereinafter further described,adjustment of the position of the several variable components also maybe made while the machine is still running. Such an adjustment may becontinuously monitored with the clearance measuring mechanism justdescribed.

The subject apparatus is therefore capable of measuring the clearancespace between cutting blades while one of these blades is rotated. Ifthis clearance space is not a desired amount, then an adjustment ofthose parts which directly affect the size of the space, specificallythe distance between the cylinder 34 and bedknife 36, must be made. Itis more desirable to move the rotating blades 32 toward the fixed blade36 since the fixed blade is at a prescribed angle and elevation which ispredetermined and fixed to give the best shearing action. The apparatusof this invention provides a unique structural arrangement which iscapable of enabling the cylinder 34 and the blades 32 attached theretoto move toward or away from the cutting zone 30 while the cylinder isrotating. This structure is best described with reference to FIGS. 2 and7.

FIG. 7 illustrates the right-hand side of a unitized structure whichcontains the cutting blades 32 and 36 as well as other components. Abase member 78 extends across substantially the entire width of theapparatus 10 and provides a support for the unitized structure heredescribed. The base member 78 is connected by bolts 80 to the main Aframe 13 of the apparatus as best shown in FIG. 2. When so attached tothe main frame, the unitized structure illustrated in FIG. 7 is capableof resisting vibrational forces normally encountered during theoperation of this apparatus, and thereby maintains the clearance spacebetween cutting blades 32 and 36 when the apparatus is operating. Inthis structural arrangement, the blade holder 38 is welded to the basemember 78 at the joint 82 shown in FIG. 2. A brace 84 is angularlypositioned between the top portion of the holder 38 and the base 78.This brace 84 is welded at its ends 86 and 88 to the base 78 and theholder 38, respectively. Thus, the fixed blade 36 is rigidly held inposition by the substantially triangularly shaped supporting arrangementprovided by the blade holder 38, the base 78, and the brace member 84.The blade 36 is adjustably connected to the holder 38 by screws 62 aswell as by the bolts 90, shown best in FIG. 7.

The rotating cylinder 34 is similarly rigidly held to the base 78through a plurality of components. The cylinder shaft which is poweredby variable speed motor 71 (FIG. 9) is carried in the bearings 68, therebeing one such bearing at each end of the shaft. The bearings 68 arebolted by means such as the bolts 92 (right side of apparatus shown inFIG. 7) to a bearing support block 94. The bearing support block 94 isin turn supported by the H block 76, and is connected thereto by lockingmeans hereinafter further described in greater detail with reference toFIGS. 11 13. The support block 94 is movable relative to the H block 76in a direction which carries the cylinder 34 closer to or further awayfrom the fixed blade 36, that is, in the direction of the arrow 95 (FIG.8). The H block 76 remains fixed to the base 78 during this movement.Such movement moves the bearing 68 and therefore the cylinder shaft 70and the cylinder 34 itself closer to the cutting blade 36 so as toreduce the clearance space between operating blades.

The mechanism for moving the cylinder is designated generally by thenumeral 96 (FIG. 7). This mechanism 96 comprises a threaded shaft 98which extends in the direction of movement of the cylinder 34 and whichis carried at opposite ends by the yoke 100. A member 104 which is hereshown as a block having an opening 106 encloses the threaded portion ofthe shaft 98 at the opening 106. The member 104 is attached to thebearing block 94 by means such as the screws 108. This block 104 isinternally threaded so as to properly mate with the thread on the shaft98. The block 104 will move relative to the threaded shaft 98 upon therotation of the latter, and since it is fixed to the bearing block 94the movement of the block 104 causes the bearing block 94 and thus thebearing 68 also to move. Similarly the cylinder 34 is caused to move byits connection to the bearing block 68. The threaded engagement of theshaft and the block 104 may be designed so that a single rotation of theshaft 98 causes a very minimal linear movement of the cylinder 34 towardthe shearing zone 30. In this way very accurate control of the positionof the cylinder may be readily obtained.

The opposite bearing 68 is simultaneously moved by the driving mechanism96 through an identical shaft and threaded member arrangement connectedto that hearing in an appropriate position as shown in FIG. 10. Thedriving linkage is through the miter gear arrangement shown generally at110 (FIG. 7). Gear 112 is connected to the shaft 98 while gear 114 isconnected to a transverse shaft 116 which extends the width of theapparatus and connects with a similar miter gear and shaft on the otherside of the apparatus identically numbered in FIG. 10.

The high degree of tracking accuracy in movement between the shaft 98and the cylinder 34 is accomplished by the structure of the member 104.This member 104, which may be composed of a suitable material as oilite,is adapted to be adjusted so that the engagement pressure of itsinternal threads against the threads of the shaft 98 may be varied. Suchadjustment is accomplished by manipulating the screws 1 18. These screwsextend through the opening 106 into the opposite section 120 of themember 104. Rotation of these screws in a clockwise direction reducesthe width of the opening 106. This necessarily increases the engagementpressure of the mating threads, and reduces backlash between the threadsto substantially zero. As a result, any calculated ratio between therotation of the shaft 98 and the linear motion of the cylinder 34 may berelied upon since there is virtually no lost motion in the connectinglinkage between these parts The entire assembly illustrated in FIG. 7may be mounted on the main supporting means 12 of the apparatus byconnecting the end sections 122 and 124 of the yoke 100 at some suitablelocation on the frame of the apparatus. This connection is preferably anonpermanent one so that the entire unit illustrated in FIG. 7 may beremoved from and assembled in the apparatus in the condition shown. Assuch, the unit represents a sub-assembly which is greatly advantageousto the manufacturer and the purchaser alike. The shaft 98 is connectedat its end 102 to another shaft 130 by the connecting gears 132. Theshaft 130 extends through the front wall 134 of the frame section 14 andthere terminates in an adjusting knob 136.

In the form specifically shown in FIGS. 9 and 10, which differs in somerespects from that in other figures, the inside wall 126 of the framesection 14 is interposed between the driving mechanism 96 and thebearing block 94 (This is not shown in the embodiment of FIG. 7, forexample). A slot 128 is placed in the wall 126 and member 104 extendsthrough the slot to its connecting point at the block 94. Thismodification is illustrated for the purposes of demonstrating othersuitable embodiments of a structure equally successful in the operationof the device, but is somewhat less advantageous than the embodiment ofFIG. 7, since disconnection of the unitized structure shown in FIG. 7from the frame section 14 is not as quickly effected with thearrangement shown in FIGS. 9 and 10.

The linear movement of the cylinder 34 during the operation of thedevice is possible because of the unique structure centering primarilyabout the support blocks 76 and 94 and the locking mechanism employed tojoin these blocks together. This particular structure is more clearlyillustrated in FIGS. 11 to 13. Referring to FIG. 11, for example, itwill be seen that this structure of H block 76 and bearing supportingblock 94 is positioned on both sides of the apparatus at each end of thecylinder 34. Reference, however, during the description of the detailedarrangement will be made to the structure on the right side only asviewed in FIG. 11.

Bock 76 comprises two upstanding vertical walls 140 and 142 which aresecured to the base plate 78, as by screws 80. A transverse wall 144 ispositioned between the walls 140 and 142 and extends rearwardlysubstantially the entire length of the elongated H block. The transversewall 144 is positioned below the upper surfaces 146 and 148 of the walls140 and 142, respectively. These upper surfaces 146 and 148 receive thelower surfaces 150 and 152 of the bearing support block 94.

This bearing support block 94 is provided with a downwardly projectingtongue section 154 which extends into the area between walls and 142 andabove the wall 144 of the H block 76. This tongue section 154effectively provides a dovetail engagement between its side walls andthe inner side walls of the upstanding walls 140 and 142. Lateralmovement of the bearing support block 94, and therefore of the cylinder34, is prevented by this engagement. The pressure of this engagement issufficient to hold the cylinder in a stationary position relative to theH block 76 and base member even when the locking mechanism hereinafterfurther described is loosened, and it is free enough to permit arelative movement of the block 94 when a force is applied such as by themechanism 96. When the locking mechanism is tightened and block 94 ismade to bear heavily against the surfaces 146 and 148 of the H block 76,a very tight engagement of the tongue section 154 and the upstandingwalls 140 and 142 is obtained, since the pressure of the bearing supportblock 94 on the walls 140 and 142 is sufiicient to slightly deform thesewalls toward the tongue section 154. A plurality of locking points isthereby accomplished.

The locking mechanism which is employed to tighten the bearing block 94against the H block 76 in the manner above described is designatedgenerally by the numeral 156, and is clearly illustrated in FIGS. 11 to13. Referring to these figures it will be seen that the lockingmechanism 156 comprises a shaft 158 to which a worm 160 is attached. Asimilar shaft 162 and worm 164 is positioned on the opposite side of theapparatus as shown. Shafts 158 and 162 are interconnected by a coupling166 which is pinned at points 168 and 169.

Referring again to the structure on the right-hand side of FIG. 11 asshown in FIGS. 12 and 13 it will be observed that the shaft 158 iscarried by a yoke 170 and passes through openings 172 and 174. The shaft158 is carried in bushings 176 and 178 in these openings, and isrotatable therein. The yoke 170 is provided with another opening 180through which a threaded bolt 182 is passed. One end of the threadedbolt 182 is affixed to the bearing support block 94 and the other end isfree-floating and is attached to a threaded collar 184 which is anintegral part of the gear 186. The H block 76 is provided with a slot188 through which the bolt 182 passes, the gear and collar beingpositioned below the H block 76. The gear 186 is in engagement with theworm 160 and is moved thereby upon the rotation of the shaft 158 or theshaft 172. Motion of these shafts may be affected from either side ofthe apparatus by turning, for example, the squared end section 190 ofshaft 158 with a ratchet wrench or the like, or alternatively rotatingthe wheel 192 which is attached to the shaft 162 (FIG. 11). The squaredsection 190 and the wheel 192 are illustrated respectively in theinterior part of frame sections 14 and 16, respectively, in FIGS. 9 and10, and are readily accessible to the operator of the apparatus.

In the operation of the locking mechanism 156, to tary motion istransmitted to the worm 160 by application of a torque to the shaft 158.This motion is transmitted to the gear 186 and causes it to rotate.Since the collar 184 of the gear 186 is held against the yoke 170 whichin turn is held against the lower surface of the H block 76, theeffective result of this rotation is to draw down the bearing supportblock 94. The movement of this block 94 is in a direction which causes atightening of engagement pressure at the surfaces 146 and 148 of the Hblock. When it is desired to loosen this connection rotation of theshaft 158 in the opposite direction will cause a reverse motion of thesupport block 94 and a subsequent loosening of the engagement pressureof that block and the H block. Thereafter, that block may be moved alongthe surfaces 146 and 148 by an actuation of the driving mechanism 96(FIG. 7).

Thus, with the construction just described the position of the rotatablecutting blades 32 may be adjusted relative to the fixed blade 36 andsuch adjustment may be carried out while the cutting blades 32 arerotating. However, it is still highly desirable and in fact veryimportant that the fibers to be sheared enter the shearing zone at anaccurate position and angle relative to the cutting blades for a propershear to be accomplished. Theoretically the best results occur when thefibers are positioned perpendicular to the two cutting blades and thecutting blades are positioned in registration with each other. Suchfiber positioning is partly influenced by the guide means 40 which isschematically illustrated in FIG. 8 and is shown in greater detail inFIGS. 3 7.

In order to obtain the best position of fibers the guide means 40 ishere provided with adjusting means which enables it to be moved upwardlyand downwardly relative to the shearing zone 30, and inwardly andoutwardly relative to that zone. The vertical movement of the guidemeans 40 is best described with reference to FIG. 5. In that figure theguide means 40 comprises an upper section 194 and a lower section 196.The section 194 is hingedly attached to the section 196 by hinge means198 at the rear portion thereof. The forward portion of section 194contains an extending nose piece 200 which, as illustrated in FIG. 8, isthat member over which the fibers pass as they enter the shearing zone30. This nose piece 200 is moved upwardly or downwardly by the motion ofthe upper section 194 relative to the lower section 196. Such motion isaccomplished by the cam mechanism generally designated 202. Thismechanism comprises eccentri cally shaped cam 204, gear 206 and the wormgear 208,the latter being fixed to the shaft 210. The shaft 210 isaccessible from the external part of the apparatus by its connection tothe extended member 212 which can project beyond the front panel of theapparatus. Rotation of the shaft 210 such as by a force applied at thesection 212 is effective to rotate the gear 208. This gear then impartsa rotary motion to the gear 206 and cam 204 to which it is connected.Upper section 194 is moved away from the lower section 196 in accordancewith the position of the cam 204. In this manner the vertical height ofthe extended nose pice 200 may be accurately adjusted in accordance withthe needs of the system. A scale 205 is mounted on the bedknife holder38 (FIG. 7) and may be used when erected to measure the exact height ofnose piece 200 relative to the center line of cylinder 34 and also toaccurately set the height of the bedknife 36.

As shown in FIG. 4 a similar carn 207 also eccentrically shaped ispositioned on the left side of the nose piece 200, and is connected to alinking shaft 203 which is covered by a sleeve 205 Rotation of the cam204 on the right side of the apparatus is transmitted through the shaft203 to the cam 207 on the left side. As a result both sides of the uppersection 194 are simultaneously moved in a vertical direction inresponse'to the single movement of shaft 210. Shaft 210 may be locked ina set position by clamping means (not shown).

The horizontal movement of the guide means 40, that is in a directiontoward or away from the shearing zone-30, is achieved by the structureillustrated best in FIGS. 3, 4 and 6. As there shown track means 214 arepositioned on opposite sides of the apparatus against the frame sections14 and 16. As most clearly illustrated in FIG. 6, the track meanscomprise an upper elongated rail 216 and a spaced lower elongated rail218. These rails definea tracking area 220 therebetween into which therollers 222 and 224 (FIG. 5) are placed. TI-Iese rollers 222 and 224 areaffixed to the lower part 196 of the guide means 40 by pins 226 and 228,respectively. Pin 226 extends into a block member 230 and is attachedthereto at one end as shown in FIG. 3. Block 230 threadably engages athreaded shaft 232 and the shaft 232 extends outwardly to the frontpanel where it is accessible at its end section 234 as shown in FIG. 1.In a manner similar to that described with reference to FIG. 7, rotationof the threaded shaft 232 causes a linear movement of the block 230along the shaft. As a result, roller 222 is carried by its attachmentthrough pin 226 along the tracking area 220 either toward shearing zoneor away from it in accordance with the direction of rotation of theshaft. Such rotary movement may be effected in part by a motor 236 whichis shown in FIG. 9. The motor 236 is deactuated by the engagement of theblock member 230 with the switch portions 238 and 240 of the limitswitches 242 and 244 respectively. These limit switches may be spaced anaccurate distance as measured by the scale 246 and the guide means 40may be automatically moved by the motor 236 when travelling betweenlimit switches. Movement beyond these limit switches in either directioncan then be carried out by a manual force applied to the end section234.

The position of limit switch 242 may be such as to automatically set thefinal position of nose piece 200.

The movement of block 230 along the shaft 232 during the travel of theguide means 40 along the tracking area 220 is transmitted to the leftside of the apparatus to a similar block 230 which moves along a similarshaft 232. The driving movement is transmitted through a transverseshaft not shown but which may be connected between the threaded shafts232 by miter gears 233 at each end thereof as illustrated in FIG. 10.With this construction equal force is generated on both sides of thenose piece permitting an even movement of the nose piece alongoppositely positioned tracks on frames 14 and 16. As shown in FIG. 10,the driving mechanism on the left side of the nose piece is identical tothat on the right side,and is similarly numbered to illustrate thecorresponding parts. The use of a motor to drive the guide means 40 isto facilitate the quick removal of the nose piece from the general areaof the shearing zone, if necessary and more specifically to aid inbringing it to the vertical position illustrated in FIG.

6. This position facilitates maintenance of the machine since the guidemeans 40,a rather bulky object, is moved out of the way thereby exposingthe interior parts of the apparatus. The guide means 40 is capable ofassuming the position shown in FIG. 6 because the track means 214 isprovided with an opening 248 at its rear part through which the rollers224 pass when the guide means 40 is moved back away from the shearingzone. The guide means 40 is pivoted on pin 226 at the front roller 222and held in a vertical position by the member 230 which still tightlyengages the threaded shaft 232 when the rear rollers 224 pass out of theopening 248. Return of the guide means 40 to its horizontal position inthe track means 214 is easily accomplished simply by lifting the nosepiece and rolling the front roller 222 along the tracking area 220 whilelifting. Once the rear roller 224 is again in position in the track 220a manual force can then be used to drive the nose piece forward untilthe motor 226 is again actuated.

The adjusting mechanisms just described are adapted to position the nosepiece 200 of the guide means 40(and thus the fibers to be cut) in avariety of locations relative to the shearing zone,since movement in twoplanes is provided. Even further improvement of the fiber position isaccomplished with the present shearing apparatus by a unique exhaustsystem which is illustrated best in FIG. 2. As there illustrated anexhaust system includes an exhaust stack 250 which is connected directlyto a narrow exhaust pipe 252, a second exhaust pipe 254, and a thirdexhaust pipe 256 which extends to a position directly below the rotatingcylinder 34. The pipe 256 is provided with an opening 258 which isadapted to receive the flock, that is, the sheared portion of the fiberswhich fall from the shearing zone 30. The opening 258 is positioneddirectly below the cylinder 34 and provides a high velocity scoop toreceive the flock. Normally in conventional systems, the air turbulencegenerated by blades 32, specifically in the pocket areas such asdesignated by the numeral 260, causes the flock to swirl in adisoriented manner and to clog components in and around the shearingzone. Furthermore, this turbulence adversely affects the position of thefibers as they enter the zone. However, with the structure illustratedin FIG. 2, a negative pressure zone is created between the shearingblade 32 and the opening 258 in the pipe 256. Such a zone is formed inpart by the brace 84. The air turbulence generated by the rotatingblades is still present, but is now used to advantage to drive the flockinto the opening 258 past the brace 84. The normally limp fibers areattracted by the negative pressure zone and are drawn to a positionnearly horizontal as they enter the cutting zone 30. They are,therefore, properly positioned and an excellent shear results. Thus, theexhaust system depicted in FIG. 2 not only clears the flock with anextremely high efficiency, but also is effective to straighten thefibers to a desired extent.

To summarize, the shearing apparatus of the invention is provided with anumber of features which function to improve to a great extent theshearing action of the apparatus. As a result, materials such as thoseused in garments which depend upon a fine and uniform finish for anattractive appearance are readily processed. Thus, synthetic fur coatsand similar items are easily fabricated with materials processed in theshearing apparatus of the invention and are thereby provided with thatlustrous, smooth finish so important in such garments.

The present apparatus provides a means to accurately measure thedistance between cutting blades in the shearing zone while the machineis in operation. This specific distance or clearance space is extremelyimportant to the proper shearing action of a device of this type. Itsaccurate control is obtained by a unique structural arrangement of theapparatus which includes a plurality of adjustment features all designedto enhance the operation of the system. For example, the rotatingcylinder may be moved to a precise position relative to the fixedcutting blade by a mechanism characterized by a lack of lost motion inthe transmission of driving force to the cylinder. A supportingstructure which carries the cylinder includes uniquely configuredsupport members which are adapted to adjust to the linear movement ofthe cylinder as well as to rigidly hold the cylinder against vibrationalforces after the new position is obtained. Moreover, the guide table ornose piece customarily employed in an apparatus of this type is providedwith mechanisms which enable it to be adjustably positioned in twoplanes relative to the cutting blades. This permits the fibers to beguided into the shearing zone at a precise angle to ensure the propershearing of all of the fibers in the material to be cut. Finally, anovel exhaust system which is designed to remove the sheared segment ofthe fibers from the area of the cylinder and out of the apparatuscooperates with the remainder of the structure already present in theapparatus to further influence the orientation of the fibers as theyenter the shearing zone.

It will be appreciated that many modifications of the apparatusdescribed may be made. Purely by way of example, the measuring systemwhich is used to monitor the clearance space between cutting blades maybe of any electromagnetic system arrangement which is designed toproduce an energy differential between blades. Moreover, any suitabletype of measuring instrument in addition to the light or meter abovedescribed obviously may be used to accurately indicate the space betweenblades. Furthermore, other types of driving mechanisms may be used tomove the several components of the apparatus. Mounting of the manycomponents may be carried out in a manner different than that describedin the drawings without adversely affecting in most instances the properoperation of the system. Additional components may also be added, suchas an exhaust fan which may be suitably positioned above the material asit enters the shearing zone to further align the fibers prior to theirentry into the zone.

While only one embodiment of the invention has been described, it willbe appreciated that other embodiments and modifications may be provided,all within the scope of the appended claims.

I claim:

1. A shearing apparatus comprising support means and a unitizedstructure operatively connected to said support means and adapted to beremoved and handled as a unit, said unitized structure comprising a basemember operatively connected to said support means, first cutting meansoperatively connected to said base member, second cutting meansoperatively to said base member and positioned thereon in cuttingrelationship relative to said first cutting means one of said cuttingmeans being rotatable relative to the other of said cutting means duringthe operation of said shearing apparatus, means mounting said one ofsaid cutting means for movement along said base member in a givendirection toward and away from the other cutting means thereby to varythe clearance space between said cutting means, said mounting meanscomprising a supporting member supporting said one cutting means, trackmeans on said base member mounting said sup porting member for movementin said given direction and adapted to prevent lateral movement of saidsupporting member in the direction of the rotary axis of said onecutting means, means for moving said supporting member along said trackmeans, adjustable locking means operatively connected between said trackmeans and said structure member and adapted to drive said supportingmember toward said track means on said base to positively lock sameagainst relative movement in said given direction, and means accessiblefrom the outside of said unitized structure for adjusting said lockingmeans.

2. The shearing apparatus of claim 1, in which said moving meanscomprises a threaded shaft extending in a direction of movement of saidone cutting means toward or away from said other cutting means, a memberthreadedly engaging said shaft and adapted to move axially of said shaftupon the rotation thereof, said member being operatively connected tosaid supporting member and effective to move said supporting member andsaid one of said cutting means when so moved.

3. In the apparatus of claim 1, said supporting member furthercomprising bearing means operatively connected to said one of saidcutting means-and effective to support said one of said cutting meansduring the rotation thereof, and a bearing support operatively connectedto said bearing means and effective to movably mount said bearing meanson said track means, said bearing means when moved being effective tocarry said one cutting means toward or away from said other cuttingmeans, thereby reducing or increasing the clearance space between saidfirst and second cutting means.

4. The shearing apparatus of claim 3, wherein said track means comprisesa block having a recess defining first and second upstanding walls eachhaving an upper surface, said upper surfaces of said first and secondwalls being effective to slidingly mount said bearing support.

5. The shearing apparatus of claim 4, in which said moving meanscomprises a threaded shah: extending in a direction of movement of saidone cutting means toward or away from said other cutting means, a

member threadedly engaging said shaft and adapted to move axially ofsaid shaft upon the rotation thereof, said member being operativelyconnected to said sup porting member and effective to move saidsupporting member and said one of s aid cutting means when so moved.

6. The shearing apparatus of claim 4, wherein said locking meanscomprises bolt means connected to said bearin su rt and ext ndin throu h'd bl k, means mov z iy connecte to sard bolt me s and ngaging saidblock and effective when driven relative to said bolt means to drivesaid block and said bearing support toward each other.

7. In the shearing apparatus of claim 6, in which said means movablyconnected to said bolt means comprises a first gearing means threadedlyengaging said bolt means, second gearing means matingly engaging saidfirst gearing means, and driving means operatively connected to saidsecond gearing means and effective to drive said gearing means therebyto adjust the relative positions of said block and bearing support.

8. The shearing apparatus of claim 4, wherein said bearing supportcomprises first and second spaced parts each engaging an upper surfaceof said first and second walls, respectively, of said block, and a thirdpart projecting downwardly into said recess of said block, said thirdpart laterally engaging said first and second walls of said block andeffective thereby to prevent lateral movement of said bearing supportrelative to said block.

9. The shearing apparatus of claim 8, wherein said locking meanscomprises bolt means connected to said bearing support and extendingthrough said block, means movably connected to said bolt means andengaging said block and effective when driven relative to said boltmeans to drive said block and said bearing support toward each other.

10.,ln the shearing apparatus of claim 9, in which said means movablyconnected to said bolt means comprises a first gearing means threadedlyengaging said bolt means, second gearing means matingly engaging saidfirst gearing means, and driving means operatively connected to saidsecond gearing means and effective to drive said gearing means therebyto adjust the relative positions of said block and bearing support.

11. The shearing apparatus of claim 10, in which said bolt means extendsthrough said third part of said bean ing support and through saidrecessed portion of said block in a direction substantially parallel tosaid first and second upstanding walls of said block, said gearing meansmoving said bolt means to increase the engagement pressure between saidbearing support and said block at said upper surface of said upstandingwalls, thereby to simultaneously increase the engagement pressure ofsaid third part against said first and second walls.

1. A shearing apparatus comprising support means and a unitizedstructure operatively connected to said support means and adapted to beremoved and handled as a unit, said unitized structure comprising a basemember operatively connected to said support means, first cutting meansoperatively connected to said base member, second cutting meansoperatively to said base member and positioned thereon in cuttingrelationship relative to said first cutting means one of said cuttingmeans being rotatable relative to the other of said cutting means duringthe operation of said shearing apparatus, means mounting said one ofsaid cutting means for movement along said base member in a givendirection toward and away from the other cutting means thereby to varythe clearance space between said cutting means, said mounting meanscomprising a supporting member supporting said one cutting means, trackmeans on said base member mounting said supporting member for movementin said given direction and adapted to prevent lateral movement of saidsupporting member in the direction of the rotary axis of said onecutting means, means for moving said supporting member along said trackmeans, adjustable locking means operatively connected between said trackmeans and said structure member and adapted to drive said supportingmember toward said track means on said base to positively lock sameagainst relative movement in said given direction, and means accessiblefrom the outside of said unitized structure for adjusting said lockingmeans.
 2. The shearing apparatus of claim 1, in which said moving meanscomprises a threaded shaft extending in a direction of movement of saidone cutting means toward or away from said other cutting means, a memberthreadedly engaging said shaft and adapted to move axially of said shaftupon the rotation thereof, said member being operatively connected tosaid supporting member and effective to move said supporting member andsaid one of said cutting means when so moved.
 3. In the apparatus ofclaim 1, said supporting member further comprising bearing meansoperatively connected to said one of said cutting means and effective tosupport said one of said cutting means during the rotation thereof, anda bearing support operatively connected to said bearing means andeffective to movably mount said bearing means on said track means, saidbearing means when moved being effective to carry said one cutting meanstoward or away from said other cutting means, thereby reducing orincreasing the clearance space between said first and second cuttingmeans.
 4. The shearing apparatus of claim 3, wherein said track meanscomprises a block having a recess defining first and second upstandingwalls each having an upper surface, said upper surfaces of said firstand second walls being effective to slidingly mount said bearingsupport.
 5. The shearing apparatus of claim 4, in which said movingmeans comprises a threaded shaft extending in a direction of movement ofsaid one cutting means toward or away from said other cutting means, amember threadedly engaging said shaft and adapted to move axially ofsaid shaft upon the rotation thereof, said member being operativelyconnected to said supporting member and effective to move saidsupporting member and said one of s aid cutting means when so moved. 6.The shearing apparatus of claim 4, wherein said locking means comprisesbolt means connected to said bearing support and extending through saidblock, means movably connected to said bolt means and engaging saidblock and effective when driven relative to said bolt means to drivesaid block and said bearing support toward each other.
 7. In theshearing apparatus of claim 6, in which said means movably connected tosaid bolt means comprises a first gearing means threadedly engaging saidbolt means, second gearing means matingly engaging said first Gearingmeans, and driving means operatively connected to said second gearingmeans and effective to drive said gearing means thereby to adjust therelative positions of said block and bearing support.
 8. The shearingapparatus of claim 4, wherein said bearing support comprises first andsecond spaced parts each engaging an upper surface of said first andsecond walls, respectively, of said block, and a third part projectingdownwardly into said recess of said block, said third part laterallyengaging said first and second walls of said block and effective therebyto prevent lateral movement of said bearing support relative to saidblock.
 9. The shearing apparatus of claim 8, wherein said locking meanscomprises bolt means connected to said bearing support and extendingthrough said block, means movably connected to said bolt means andengaging said block and effective when driven relative to said boltmeans to drive said block and said bearing support toward each other.10. In the shearing apparatus of claim 9, in which said means movablyconnected to said bolt means comprises a first gearing means threadedlyengaging said bolt means, second gearing means matingly engaging saidfirst gearing means, and driving means operatively connected to saidsecond gearing means and effective to drive said gearing means therebyto adjust the relative positions of said block and bearing support. 11.The shearing apparatus of claim 10, in which said bolt means extendsthrough said third part of said bearing support and through saidrecessed portion of said block in a direction substantially parallel tosaid first and second upstanding walls of said block, said gearing meansmoving said bolt means to increase the engagement pressure between saidbearing support and said block at said upper surface of said upstandingwalls, thereby to simultaneously increase the engagement pressure ofsaid third part against said first and second walls.